CN105190202B - Heat exchanger and refrigerating circulatory device - Google Patents
Heat exchanger and refrigerating circulatory device Download PDFInfo
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- CN105190202B CN105190202B CN201380076370.7A CN201380076370A CN105190202B CN 105190202 B CN105190202 B CN 105190202B CN 201380076370 A CN201380076370 A CN 201380076370A CN 105190202 B CN105190202 B CN 105190202B
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- refrigerant
- flat tube
- heat exchanger
- flow path
- evaporator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/04—Condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
- F28D1/0475—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend
- F28D1/0476—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend the conduits having a non-circular cross-section
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
- F25B39/028—Evaporators having distributing means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
- F28D2021/007—Condensers
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
At least more than two layers of flat tube (101) is bent in the end side of direction of principal axis, or it is connected with the flat tube of other layers, the flat tube (101) of at least two row above is connected with the flat tube (101) that other are arranged, so as to form the refrigerant flow path for refrigerant flowing, it is configured in the case where the heat exchanger uses as condenser, the circulating direction of refrigerant flow path flowing in a column direction and gas turns into opposite stream.
Description
Technical field
The present invention relates to heat exchanger and refrigerating circulatory device.
Background technology
In existing technology, it is proposed that for example following heat exchanger, that is, have：First set collector and second set
Collector, the first set collector and second set collector are erect respectively to be set；Multiple flat tubes, the multiple flat tube are upper and lower
It is arranged in that side is opposite, one end of each flat tube is connected to above-mentioned first set collector, and the other end is connected to above-mentioned second set
Collector, and internally form the path of refrigerant；And multiple fin, the multiple fin is by adjacent above-mentioned flat tube
Between be divided into multiple ventilation path (such as referenced patent document 1) for air flow.
Prior art literature
Patent document
Patent document 1：No. 5071597 publications (claim 1) of Japanese Patent No.
The content of the invention
The invention problem to be solved
Using the heat exchanger of flat tube compared with the situation for having used pipe, the flowing resistance of air reduces heat-transfer pipe, because
This arrangement spacing by reducing heat-transfer pipe, can configure heat-transfer pipe to high-density., can by the high-density installation of heat-transfer pipe
Fin efficiency is improved, passes through the expansion of the heat transfer area in the pipe of heat-transfer pipe, it is possible to increase the heat transfer property of heat exchanger.
But if heat-transfer pipe uses flat tube, flowing path section area reduces, the number of the arrangement increase of flat tube, so as to flat
The stream total length of pipe is elongated, therefore the refrigerant pressure loss increase in pipe.Therefore, it is necessary to increase branch's number of refrigerant
Amount, increase refrigerant flow path quantity (number of passages).
Therefore, in the technology of above-mentioned patent document 1, the distributor of collection cast has been used to distribute refrigerant to stream.
The partition characteristic of the distributor of the collection cast used all the time is different according to the internal circulating load of refrigerant.Cause
This, in the heat exchanger for having used the very more flat tube of numbers of branches, refrigerant is evenly distributed to all refrigerant flow paths
More difficult, the performance that heat exchanger be present reduces the problem of such.
In addition, in the case where using heat exchanger as evaporator, the refrigerant condition in the porch of heat exchanger
For biphase gas and liquid flow, so if numbers of branches increases, then existing to evenly distribute becomes the problem of difficult such.In addition, by
In the case that multiple row heat-transfer pipe constitutes heat exchanger, numbers of branches can further increase, exist evenly distribute become it is difficult this
The problem of sample.
In addition, if the refrigerant pressure loss increase in the pipe of flat tube, then pass through the refrigerant flow path of heat exchanger
The pressure of refrigerant reduces, and the temperature of refrigerant reduces therewith.So during refrigerant is by heat exchanger there occurs
In the case of temperature change, it is desirable to suppress the reduction of the heat transfer property of heat exchanger.
In addition, if the refrigerant for the refrigerant flow path for passing through heat exchanger is less than 0 DEG C, then heat is carried out with refrigerant sometimes
The moisture contained in the gas of exchange can condense, and form frost and be attached on the surface of heat exchanger.If frost is attached to hot friendship
On parallel operation, then the heat transfer property that heat exchanger be present reduces the problem of such.
The present invention completes to solve the problems, such as described above, obtains easily to refrigerant flow path uniformly dividing
Heat exchanger and refrigerating circulatory device with refrigerant.In addition, obtain suppressing the reduction of the heat transfer property of heat exchanger
Heat exchanger and refrigerating circulatory device.
Means for solving the problems
The heat exchanger of the present invention possesses：Multiple fin, the multiple fin be spaced compartment of terrain configuration, supplied gas
Flow in-between；And multiple flat tubes, the multiple flat tube are inserted into above-mentioned multiple fin, for being carried out with above-mentioned gas
The refrigerant flowing of heat exchange, above-mentioned multiple flat tubes configure multilayer on the layer direction that the circulating direction with above-mentioned gas intersects,
And multiple row is configured on the column direction along the circulating direction of above-mentioned gas, at least more than two layers of above-mentioned flat tube is in direction of principal axis
End side be bent, or be connected with the above-mentioned flat tube of other layers, above-mentioned flat tubes more than at least two row arrange upper with other
Flat tube connection is stated, so as to form the refrigerant flow path for the flowing of above-mentioned refrigerant, is configured in the heat exchanger as condenser
In the case of use, the circulating direction of the flowing in a column direction of above-mentioned refrigerant flow path and above-mentioned gas turns into opposite stream.
The effect of invention
The present invention easily can evenly distribute refrigerant to refrigerant flow path.In addition, the present invention can suppress heat exchanger
Heat transfer property reduction.
Brief description of the drawings
Fig. 1 is the figure of the structure for the air regulator for representing embodiments of the present invention 1.
Fig. 2 is the stereogram of the heat exchanger of embodiments of the present invention 1.
Fig. 3 is the sectional view of the flat tube of embodiments of the present invention 1.
Fig. 4 is the figure of the refrigerant flow path for the heat exchanger for illustrating embodiments of the present invention 1.
Fig. 5 is to schematically show the refrigerant when heat exchangers of embodiments of the present invention 1 uses as condenser
Flow direction and air flow direction figure.
Fig. 6 is to represent the air and refrigerant when the heat exchangers of embodiments of the present invention 1 uses as condenser
The figure of temperature change.
Fig. 7 is to represent the air and refrigerant when the heat exchangers of embodiments of the present invention 1 uses as evaporator
The figure of temperature change.
Fig. 8 is represented the heat exchanger of embodiments of the present invention 1 shape of the bending machining into L-shaped in a column direction
The top view of state.
Fig. 9 is the figure of the other structures for the heat exchanger for representing embodiments of the present invention 1.
Embodiment
Embodiment 1
(air regulator)
Fig. 1 is the figure of the structure for the air regulator for representing embodiments of the present invention 1.
In embodiment 1, an example as the refrigerating circulatory device of the present invention illustrates to air regulator.
As shown in figure 1, air regulator possesses refrigerant loop, the refrigerant loop is sequentially connected using refrigerant piping
Compressor 600, four-way valve 601, outdoor heat exchanger 602, expansion valve 604 and indoor side heat exchanger 605, and make refrigerant
Circulation.
In addition, air regulator possesses the outdoor fan 603 that air (outdoor air) is sent into outdoor heat exchanger 602
With the indoor fan 606 that air (room air) is sent into indoor side heat exchanger 605.
In addition, " expansion mechanism " of the expansion valve 604 equivalent to the present invention.
Four-way valve 601 carries out heating operation, refrigeration fortune by switching the flow direction of the refrigerant in refrigerant loop
The switching turned.In addition, in the case of single cold or singly warm air regulator, four-way valve 601 can also be omitted.
Indoor side heat exchanger 605 is equipped on indoor set.Indoor side heat exchanger 605 is used as refrigeration in cooling operation
The evaporator of agent.The condenser as refrigerant in heating operation of indoor side heat exchanger 605.
Outdoor heat exchanger 602 is equipped on outdoor unit.Outdoor heat exchanger 602 is used as utilizing in cooling operation
The heat of refrigerant heats the condenser of air etc..Outdoor heat exchanger 602 is used as evaporating refrigerant in heating operation
And using heat of gasification now come the evaporator of cooling air etc..
Compressor 600 is compressed to the refrigerant discharged from evaporator, is made high temperature and is supplied to condenser.
Expansion valve 604 makes the refrigerant expansion from condenser discharge, makes low temperature and is supplied to evaporator.
Illustrate the heating operation of air regulator and the action of the refrigerant of cooling operation below.
The action ＞ of refrigerant during ＜ heating operations
In heating operation, four-way valve 601 is switched to Fig. 1 state shown in solid.Then, from the row of compressor 600
The refrigerant of the HTHP gone out flows into indoor side heat exchanger 605 by four-way valve 601.Indoor side heat exchanger 605 exists
As condenser working during heating operation, thus flow into the refrigerant of indoor side heat exchanger 605 with from indoor fan 606
Room air carries out heat exchange and radiated, and so as to which temperature reduces the liquid refrigerant as supercooled state, and is handed over from indoor heat
Parallel operation 605 flows out.
The refrigerant flowed out from indoor side heat exchanger 605 is depressurized by expansion valve 604 and turns into gas-liquid two-phase cold-producing medium, and
Flow into outdoor heat exchanger 602.Outdoor heat exchanger 602 as evaporator operation, therefore flows into room in heating operation
The refrigerant of outside heat exchangers 602 carries out heat exchange with the outdoor air from outdoor fan 603 and absorbed heat, evaporates, so as to
As the refrigerant of gaseous state, and flowed out from outdoor heat exchanger 602.The refrigeration flowed out from outdoor heat exchanger 602
Agent is inhaled into compressor 600 by four-way valve 601.
The action ＞ of refrigerant during ＜ cooling operations
In cooling operation, four-way valve 601 is switched to the state shown in Fig. 1 dotted line.The height discharged from compressor 600
The refrigerant of warm high pressure flows into outdoor heat exchanger 602 by four-way valve 601.Outdoor heat exchanger 602 is transported in refrigeration
As condenser working when turning, therefore flow into the refrigerant of outdoor heat exchanger 602 and the outdoor sky from outdoor fan 603
Gas carries out heat exchange and radiated, so as to which temperature reduces the liquid refrigerant as supercooled state, and from outdoor heat exchanger 602
Outflow.
The refrigerant flowed out from outdoor heat exchanger 602 is depressurized by expansion valve 604 and turns into gas-liquid two-phase cold-producing medium, is flowed
Enter indoor side heat exchanger 605.Indoor side heat exchanger 605 as evaporator operation, therefore flows into indoor in cooling operation
The refrigerant of side heat exchanger 605 with from indoor fan 606 room air carry out heat exchange after heat absorption, evaporation, from into
For the refrigerant of gaseous state, and flowed out from indoor side heat exchanger 605.The refrigerant flowed out from indoor side heat exchanger 605
Compressor 600 is inhaled into by four-way valve 601.
(heat exchanger)
Illustrate heat exchange used at least one party of outdoor heat exchanger 602 and indoor side heat exchanger 605 below
The structure of device.
Fig. 2 is the stereogram of the heat exchanger of embodiments of the present invention 1.
As shown in Fig. 2 heat exchanger possesses multiple fin 100 and multiple flat tubes 101.The heat exchanger is used to be led to
The heat exchange of the gases such as the air crossed between multiple fin 100 and the refrigerant of circulation in multiple flat tubes 101.
Fin 100 is for example made of aluminum, has plate-like shape.Fin 100 be laminated at a prescribed interval it is multiple, for sky
The gases such as gas circulate in-between.In addition, the opening for inserting multiple flat tubes 101 respectively is formed on fin 100, at this
Opening is inserted flat tube 101 and engaged with multiple flat tubes 101.
Multiple flat tubes 101 are for example made of aluminum, are the heat-transfer pipes that cross section profile is flat pattern.Multiple flat tubes 101 with
Multilayer is configured on the layer direction that the circulating direction of air intersects, and configuration is more on the column direction along the circulating direction of air
Row.Flat tube 101 is with circulating direction (column direction) of the direction of the major axis of flat pattern towards air, the short axle in flat pattern
The mode of interval is configured with multiple on direction (layer direction).In addition, flat tube 101 is flat with adjacent column for example on layer direction
Pipe 101 alternately arranges (zigzag arrangement).
In the example shown in Fig. 2, multiple flat tubes 101 are configured to two row.In addition, the number of plies of multiple flat tubes 101 will be
Illustrate afterwards.
Fig. 3 is the sectional view of the flat tube of embodiments of the present invention 1.
As shown in figure 3, multiple streams 201 by separator lined are formd in flat tube 101.For example, the stream in flat tube 101
The cross sectional shape on road 201 is formed as a generally rectangular, and the width of the stream 201 on the short-axis direction of flat tube 101 is a, in major axis
Width on direction is b.
In addition, in fig. 2, in a side of heat exchanger, flat tube 101 is connected with collector 102.In addition, in heat exchanger
Another side, flat tube 101 has in the end side of direction of principal axis is for example bent to the shape of U-shaped.That is, it is adjacent in same row
The flat tube 101 for connecing two layers of configuration is made up of a flat tube 101 for being bent to U-shaped.
Although in addition, illustrating to bend to flat tube 101 into the situation of U-shaped herein, the present invention is not limited to this.Such as
The end of the direction of principal axis of flat tube 101 can also be connected with another layer of flat tube 101 using U-bend etc..
Refrigerant piping 103 and refrigerant piping 104 are connected in collector 102.Used in heat exchanger as condenser
In the case of, collector 102 is enabled its flow into from the refrigerant branch that refrigerant piping 103 flows into multiple refrigerant flow paths
Flat tube 101.Then, the refrigerant for having passed through multiple flat tubes 101 is made to collaborate and be flowed out from refrigerant piping 104.
In addition, in the case where heat exchanger uses as evaporator, the flow direction of refrigerant is opposite with the above situation.
Fig. 4 is the figure of the refrigerant flow path for the heat exchanger for illustrating embodiments of the present invention 1.Figure 4 illustrates from
Observe the sectional view of heat exchanger in the side of collector 102.
As shown in figure 4, it is provided with inflow entrance 302, across row streams 303, flow export 304 in collector 102.
An end of the flat tube 101 for being bent to U-shaped is connected in inflow entrance 302.Connected in across row streams 303 curved
Another end of the bent flat tube 101 into U-shaped.In addition, the flat tube 101 of adjacent column is connected with each other by across row streams 303.Flowing
Road 303 connects another end for the flat tube 101 for being bent to U-shaped.
So, form one by least more than two layers of flat tube 101 and the flat tube 101 of at least two row above and supply refrigerant
The refrigerant flow path (path) of flowing.
In addition, in the above description, illustrate to form one for refrigeration by two layers of row flat tube 101 of flat tube 101 and two
The situation of the refrigerant flow path (path) of agent flowing, but the present invention is not limited to this.For example, it is also possible to it will configure in same row
Multiple flat tubes 101 end be connected with each other, a refrigerant flow path is formed by more than two layers of flat tube 101.
That is, the number of plies (number of plies/number of vias) of the flat tube 101 of each refrigerant flow path is more than two layers.
In addition, in the above description, illustrate to be provided with the situation of across row streams 303, but the present invention in collector 102
It is not limited to this.Such as can also using U-bend etc. come by the side end of collector 102 of flat tube 101 and other row flat tubes 101
Connection.
Fig. 5 is to schematically show the refrigerant when heat exchangers of embodiments of the present invention 1 uses as condenser
Flow direction and air flow direction figure.
As shown in figure 5, in the case where heat exchanger uses as condenser, collector 102 is flowed into from refrigerant piping 103
Refrigerant multiple streams are branched to by the branch flow passage in collector 102, and flow into flat tube 101 from inflow entrance 302 respectively.
The refrigerant for having flowed into flat tube 101 flows into collector via the stream 301 of turning back for the flat tube 101 for being bent to U-shaped
102 across row streams 303.
The refrigerant for having flowed into across row streams 303 flows into the flat tube 101 of adjacent column, via the stream 301 of turning back of the row, from
Flow export 304 flows into collector 102.
The refrigerant that collector 102 is flowed into from flow export 304 is collaborated into a stream by the interflow stream in collector 102
Road, and flowed out from refrigerant piping 104.
In addition, in the case where heat exchanger uses as evaporator, the flow direction of refrigerant is opposite with the above situation.
In addition, in the case where heat exchanger uses as condenser, the flow direction relative to air is being passed to
After the flat tube 101 of the row in downstream, it can be flowed in the flat tube 101 of the row of upstream side.That is, the row side of refrigerant flow path
To flowing and the circulating direction of air turn into opposite stream.
As described above, at least more than two layers of flat tube 101 is bent in the end side of direction of principal axis, or it is flat with other layers
Pipe 101 is connected, and at least the flat tube 101 of the two row above is connected with other flat tubes 101 arranged, so as to form the system for refrigerant flowing
Refrigerant line.
Therefore, compared with constituting the situation of refrigerant flow path (path) to each flat tube 101, number of vias can be reduced
Amount, easily can evenly distribute refrigerant to each refrigerant flow path.Further, since number of passages is reduced, collector can be also reduced
The numbers of branches of refrigerant in 102, it can easily evenly distribute refrigerant using the distributor of collection cast.
In addition, the stream 301 of turning back of refrigerant uses the flat tube 101 for being bent to U-shaped, so as to can correspondingly increase
The effective heat transfer area of heat exchanger, improve heat transfer property.
In addition, flat tube 101 is formed into stream 301 of turning back in the end lateral bend of direction of principal axis, without in flat tube 101
The both sides of direction of principal axis collector 102 etc. is set, by increasing capacitance it is possible to increase the effective heat transfer area of heat exchanger, it is possible to increase heat transfer property.
Further, since the both sides without the direction of principal axis in flat tube 101 set collector 102 etc., so heat exchange can be reduced
The installation space of device.
In addition, flat tube 101 is formed into stream 301 of turning back in the end lateral bend of direction of principal axis, so as in stream 301 of turning back
The upper junction surface in the absence of pipe arrangement, therefore, the risk of refrigerant leakage reduce.
Illustrate the temperature change of the air and refrigerant when heat exchanger uses as condenser below.
Fig. 6 is to represent the air and refrigerant when the heat exchangers of embodiments of the present invention 1 uses as condenser
The figure of temperature change.
As shown in fig. 6, in the case where heat exchanger uses as condenser, pass through the sky between multiple fin 100
Gas is gradually increasing by the refrigerant heat by multiple flat tubes 101, temperature.
On the other hand, by the refrigerant of multiple flat tubes 101 because the pressure loss (friction loss) in pipe arrangement is and pressure
Reduce, temperature gradually reduces therewith.In the case where heat exchanger uses as condenser, the flowing of refrigerant in a column direction
It is from the downstream of the flow direction relative to air (air side heat exchanger outlet) towards the flow direction relative to air
Upstream side (air side heat exchanger entrance) circulation.
Therefore, the air side heat exchanger outlet having been had gone up in the temperature of air, the temperature of refrigerant is high, in air
Air side heat exchanger entrance before temperature rising, the temperature of refrigerant are low.That is, used in heat exchanger as condenser
In the case of, make the flowing of air with the flowing of refrigerant in a column direction be opposite stream, so as to ensure all the time refrigerant with
The temperature difference of air.
The heat transfer property of heat exchanger when being used therefore, it is possible to improve as condenser.
Illustrate the temperature change of the air and refrigerant when heat exchanger uses as evaporator below.
Fig. 7 is to represent the air and refrigerant when the heat exchangers of embodiments of the present invention 1 uses as evaporator
The figure of temperature change.
As shown in fig. 7, in the case where heat exchanger uses as evaporator, pass through the sky between multiple fin 100
By being cooled down by the refrigerant of multiple flat tubes 101, temperature gradually reduces gas.
On the other hand, by the refrigerant of multiple flat tubes 101 because the pressure loss (friction loss) in pipe arrangement is and pressure
Reduce, temperature gradually reduces therewith.In the case where heat exchanger uses as evaporator, the flowing of refrigerant in a column direction
It is from the upstream side of the flow direction relative to air (air side heat exchanger entrance) towards the flow direction relative to air
Downstream (air side heat exchanger outlet) circulation.That is, the circulation side of refrigerant flow path flowing in a column direction and air
To as parallel stream.
Therefore, the air side heat exchanger entrance before the temperature of air reduces, the temperature of refrigerant is high, in air
Air side heat exchanger outlet after temperature reduction, the temperature of refrigerant are low.That is, used in heat exchanger as evaporator
In the case of, it is parallel stream to make the flowing of air and the flowing of refrigerant in a column direction, so as to ensure all the time refrigerant with
The temperature difference of air.
The heat transfer property of heat exchanger when being used therefore, it is possible to improve as evaporator.
Here, in the case where heat exchanger uses as evaporator, if the temperature (evaporating temperature) of refrigerant is less than 0
DEG C, then carrying out the moisture that contains in the air of heat exchange with refrigerant sometimes can condense, and form frost and be attached to fin 100 and flat
On pipe 101.Therefore, in order to prevent frost attachment on the heat exchanger, it is necessary to which evaporating temperature is maintained at into more than 0 DEG C.
As described above, by the refrigerant of multiple flat tubes 101 because the pressure loss (friction loss) in pipe arrangement is and pressure
Reduce, temperature is gradually reduced therewith.
The heat exchanger of present embodiment 1 constitutes the system flowed for refrigerant by least more than two layers of flat tube 101
Refrigerant line.Therefore, if the number of plies for forming the flat tube 101 of a refrigerant flow path is excessive, the stream of a cold-producing medium stream
Length is with regard to elongated, and the pressure loss increases therewith.
Due to such situation, so the number of plies (number of plies/number of vias) of the flat tube 101 of each refrigerant flow path is set
The evaporating temperature determined the pressure loss of the refrigerant into due to a refrigerant flow path and reduced is higher than 0 DEG C.
In other words, the number of plies (number of plies/number of vias) of the flat tube 101 of each refrigerant flow path is as steaming in heat exchanger
In the case of hair device use, make the number of plies of the pressure loss of refrigerant in a refrigerant flow path below setting.Below
It is specifically described.
In general, it is known that friction loss (pressure loss) the Δ P in the pipe of the single-phase refrigerant flowing of gasf[Pa] by
Following formula (1) represents.
[formula 1]
f：The friction loss factor [-] of pipe
l：The length [m] of stream
De：The hydraulic diameter [m] of pipe
ρv：Density [the kg/m of the single-phase refrigerant of gas3]
u：In the flow velocity [m/s] of the fluid of Bottomhole pressure
The friction loss factor f of pipe is generally 0.01 or so.
Flow velocity u in pipe can be calculated by following formula (2).
[formula 2]
G：The internal circulating load [kg/s] of refrigerant
The internal circulating load of refrigerant uses the circulation of the refrigerant of inflow heat exchanger in the specified operating of air regulator
Measure (maximum).That is, calculated under conditions of the pressure loss is maximum.
Here, such as G=60 × hp.
hp：The horsepower [kg/h] of air regulator
In order to which the phenomenon in the stream of complexity is converted into pipe flow similar on mechanics, hydraulic diameter De is defined as
Act on that the situation of the ratio between the pressure of flowing path section and the fluid friction of wetted perimeter and pipe is equal, represented by following formula (3).
[formula 3]
A：Flowing path section area [m2]
C：Wetted perimeter length [m]
It is as shown in Figure 3 flat tube 101 be internally formed multiple streams 201 in the case of, hydraulic diameter De can profit
Calculated with the major axis a and short axle b of a stream 201 by following formula (4).
[formula 4]
The flow path length l of each refrigerant flow path (each path) of heat exchanger can be by following formula (5)
Calculate.
[formula 5]
L：Stack length [m]
Dn：The number of plies of flat tube 101
Nr：The columns of flat tube 101
Np：Refrigerant flow path quantity (number of passages)
Stack length L is the distance from the end of the side of collector 102 to the end for being bent to U-shaped side of flat tube 101.
In the case where heat exchanger uses as evaporator, there is gas-liquid two-phase cold-producing medium circulation in flat tube 101.Gas-liquid
Friction loss Δ P [Pa] in the pipe of two-phase refrigerant flow can utilize the friction in the pipe of the single-phase refrigerant flowing of gas
Lose Δ PfFriction loss increase coefficient Φ v [-] in [Pa] and biphase gas and liquid flow are calculated by following formula (6).
[formula 6]
Δ P=Δs Pf·φV 2…(6)
Friction loss increase coefficient Φ v in biphase gas and liquid flow are calculated by following formula (7), formula (8).
[formula 7]
φV 2=1+21X+X2…(7)
[formula 8]
x：The mass dryness fraction [-] of refrigerant
ρv：Density [the kg/m of gas3]
ρL：Density [the kg/m of liquid3]
ηv：The viscosity [Pas] of gas
ηL：The viscosity [Pas] of liquid
The mass dryness fraction x of refrigerant is for example using the mass dryness fraction for the refrigerant for flowing into evaporator and putting down for the mass dryness fraction of the refrigerant of outflow
Average.Such as the mass dryness fraction x of refrigerant is 0.6 or so.
The density p of gasvIt is minimum in the temperature of the refrigerant of inflow heat exchanger according to the physical property values of refrigerant
Determined under conditions of value.That is, it is false in the temperature as the refrigerant of inflow heat exchanger according to specification of air regulator etc.
If minimum temperature under conditions of calculated.
Operating condition regardless of air regulator, the density p of liquidL, gas viscosities ilv, liquid viscosities ilLAll
It is similar to constant, is determined according to the physical property values of refrigerant.
Here, in order to prevent frost attachment on the heat exchanger, it is necessary to which evaporating temperature is maintained at into more than 0 DEG C.That is, saturation is steamed
Stripping temperature is needed more than 0 DEG C.
Therefore, it is necessary to make friction loss (pressure loss) the Δ P of refrigerant flow pathfCaused pressure is reduced in following difference
Value is following, i.e., is pressure under conditions of minimum value and the difference of saturation pressure in the temperature of the refrigerant of inflow heat exchanger.
If it is defined higher limit P to make the differencemax[Pa], then friction loss (pressure loss) Δ PfNeed meet with
Under formula (9).
[formula 9]
ΔP≤Pmax…(9)
For example, in the case where the temperature of the refrigerant of inflow heat exchanger is 5 DEG C, if the pressure due to refrigerant flow path
Power loss causes saturated-steam temperature to be reduced to 0 DEG C, then pressure during inflow heat exchanger and the difference of saturation pressure are 100
[kPa] left and right.
Formula (1)~(9) more than, the number of plies (number of plies/number of vias) of the flat tube 101 of each refrigerant flow path need
Meet following formula (10).
[formula 10]
The Section 1 on the right of above-mentioned formula (10) can be regarded as described above according to the specification and refrigerant of air regulator
The determination such as physical property constant K.In addition, flowed because forming one by least more than two layers of flat tube 101 for refrigerant
Refrigerant flow path, therefore, the number of plies (number of plies/number of vias) of the flat tube 101 of each refrigerant flow path is more than two layers.
In summary, the number of plies (number of plies/number of vias) of the flat tube 101 of each refrigerant flow path meets following formula
(11)。
[formula 11]
Dn：The number of plies of flat tube 101
Np：Refrigerant flow path quantity (number of passages)
De：The hydraulic diameter [m] of flat tube
n：The quantity of stream 201 in flat tube 101
L：Stack length [m]
Nr：The columns of flat tube 101
Pmax：Defined higher limit [Pa]
ρv：Saturated vapor density [kg/m under the evaporating temperature of refrigerant3]
G：The internal circulating load [kg/h] of the refrigerant of inflow heat exchanger
x：The mass dryness fraction [-] of refrigerant
The friction loss increase coefficient [-] of two phase flow
f：The friction loss factor [-] of pipe
If in addition, higher limit P as defined in makingmaxFor 100 [kPa], make internal circulating load G=60 × hp [kg/h] of refrigerant,
Then constant K can be approximated to be for example following formula (12).
[formula 12]
The right side (upper limit) of above-mentioned formula (11) includes hydraulic diameter De 5 powers, the flat tube of each refrigerant flow path
The upper limit of 101 number of plies (number of plies/number of vias) is most influenceed by the hydraulic diameter De of flat tube 101.That is, each refrigerant flow path
Flat tube 101 the number of plies (number of plies/number of vias) be at least hydraulic diameter De based on flat tube 101 value, be in the heat exchanger
In the case of being used as evaporator, the pressure loss that makes refrigerant in a refrigerant flow path be the layer below setting
Number.
As described above, the number of plies of the flat tube 101 of each refrigerant flow path is configured to, used flowing into as evaporator
Heat exchanger refrigerant internal circulating load G be maximum, inflow heat exchanger refrigerant temperature be minimum value condition
Under, the evaporating temperature for making to reduce due to the pressure loss of the refrigerant in a refrigerant flow path is higher than 0 DEG C.
Therefore, in the case where heat exchanger is used as evaporator, it can prevent that the reduction due to evaporating temperature from leading
The white attachment of cause, can prevent the reduction of the heat transfer property of heat exchanger.
(shape of heat exchanger)
Illustrate the shape of heat exchanger below.
Fig. 8 is represented the heat exchanger of embodiments of the present invention 1 state of the bending machining into L-shaped in a column direction
Top view.
As shown in figure 8, multiple fin 100 are arranged on each layer of multiple flat tubes 101.Also, multiple flat tubes 101
Processing can be bent at least the one of direction of principal axis.It is processed into addition, showing to be bent in a column direction in the example of fig. 8
The situation of L-shaped, but the present invention is not limited to this.Such as it can also be bent and be processed into U-shaped, quadrangle.
One end of multiple flat tubes 101 is bent to U-shaped by the heat exchanger of present embodiment 1, by another end
Enter row set by collector 102 to connect.
Thus, for example as shown in figure 8, the different bending machining of curvature can be carried out in each row.
(variation)
Fig. 9 is the figure of the other structures for the heat exchanger for representing embodiments of the present invention 1.
As shown in figure 9, above-mentioned collector 102 can also be replaced using possessing the structure such as lower member：By refrigerant branch
Distributor 701, be arranged on flat tube 101 end multiple y-bend branched pipes 703 and connection distributor 701 and multiple y-bends
The capillary 702 of branched pipe 703.
In the structure shown here, also have in a side of heat exchanger (right side of figure), flat tube 101 in the end side of direction of principal axis
Such as it is bent to the shape of U-shaped.In addition, in the another side (left side of figure) of heat exchanger, pass through y-bend branched pipe 703
It will be connected with each other between the flat tube 101 of adjacent layer.
By such structure, can also reach and said structure identical effect.
In addition, in present embodiment 1, an example as the refrigerating circulatory device of the present invention enters to air regulator
Explanation is gone, but the present invention is not limited to this.Such as refrigerating plant, heat pump assembly etc. can also be applied to, form refrigerant time
Road simultaneously has other refrigerating circulatory devices as evaporator, the heat exchanger of condenser.
Description of reference numerals
100 fin, 101 flat tubes, 102 collectors, 103 refrigerant pipings, 104 refrigerant pipings, 201 streams, 301 turn back
Stream, 302 inflow entrances, 303 across row streams, 304 flow exports, 600 compressors, 601 four-way valves, 602 outdoor heat exchangers,
603 outdoor fans, 604 expansion valves, 605 indoor side heat exchangers, 606 indoor fans, 701 distributors, 702 capillaries, 703 2
Pitch branched pipe.
Claims (5)
1. a kind of heat exchanger, possesses：
Multiple fin, the multiple fin are spaced compartment of terrain configuration, and supplied gas flows in-between；
Multiple flat tubes, the multiple flat tube are inserted into the multiple fin, the refrigeration for carrying out heat exchange with the gas
Agent is flowed；And
Multiple streams, the multiple stream are formed at each flat tube,
The multiple flat tube configures multilayer on the layer direction that the circulating direction with the gas intersects, and along the gas
Multiple row is configured on the column direction of the circulating direction of body,
At least more than two layers of the flat tube is bent in the end side of direction of principal axis, or is connected with the flat tube of other layers,
The flat tubes more than at least two row is connected with the flat tube that other are arranged, so as to form the refrigerant for refrigerant flowing
Stream,
The quantity of the refrigerant flow path, the number of plies of the flat tube, each stream in the flat tube hydraulic diameter,
The stack length of stream quantity, the flat tube and the columns of the flat tube in the flat tube meet following formula (1)
Relation,
[formula 1]
<mrow>
<mn>2</mn>
<mo>&le;</mo>
<msub>
<mi>D</mi>
<mi>n</mi>
</msub>
<mo>/</mo>
<msub>
<mi>N</mi>
<mi>p</mi>
</msub>
<mo>&le;</mo>
<mi>K</mi>
<mo>&CenterDot;</mo>
<mfrac>
<mrow>
<msup>
<mi>De</mi>
<mn>5</mn>
</msup>
<mo>&times;</mo>
<msup>
<mrow>
<mo>(</mo>
<msub>
<mi>N</mi>
<mi>p</mi>
</msub>
<mo>&times;</mo>
<mi>n</mi>
<mo>)</mo>
</mrow>
<mn>2</mn>
</msup>
</mrow>
<mrow>
<mi>L</mi>
<mo>&times;</mo>
<msub>
<mi>N</mi>
<mi>r</mi>
</msub>
</mrow>
</mfrac>
<mn>...</mn>
<mrow>
<mo>(</mo>
<mn>1</mn>
<mo>)</mo>
</mrow>
</mrow>
Here,
DnIt is the number of plies of the flat tube,
NpIt is the quantity of the refrigerant flow path,
K be by being used in the heat exchanger as evaporator in the case of the refrigerant in a refrigerant flow path
The constant that the higher limit of the pressure loss determines,
De is the hydraulic diameter of each stream in the flat tube,
N is the stream quantity in the flat tube,
L is the stack length of the flat tube,
NrIt is the columns of the flat tube.
2. heat exchanger according to claim 1, it is characterised in that
Be configured in the case where the heat exchanger uses as condenser, the flowing of the refrigerant flow path in a column direction with
The circulating direction of the gas turns into opposite stream.
3. heat exchanger according to claim 1 or 2, it is characterised in that
The multiple fin is arranged on each layer of the multiple flat tube,
Processing is bent at least the one of the direction of principal axis of the multiple flat tube.
4. a kind of refrigerating circulatory device, possess and be sequentially connected compressor, condenser, expansion mechanism and evaporator simultaneously using pipe arrangement
Make the refrigerant loop of refrigerant circulation,
At least one party of the condenser and the evaporator has used the heat exchanger any one of claims 1 to 3.
5. a kind of refrigerating circulatory device, possess and be sequentially connected compressor, condenser, expansion mechanism and evaporator simultaneously using pipe arrangement
Make the refrigerant loop of refrigerant circulation,
At least described evaporator in the condenser and the evaporator has been used any one of claims 1 to 3
Heat exchanger,
The number of plies of the evaporator, each refrigerant flow path flat tube is configured to, and is flowing into the evaporation
The condition that the internal circulating load of the refrigerant of device is maximum, the temperature for the refrigerant for flowing into the evaporator is minimum value
Under, the evaporating temperature for making to reduce due to the pressure loss of the refrigerant in a refrigerant flow path is higher than 0 DEG C.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2013/062934 WO2014181400A1 (en) | 2013-05-08 | 2013-05-08 | Heat exchanger and refrigeration cycle device |
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| Publication Number | Publication Date |
|---|---|
| CN105190202A CN105190202A (en) | 2015-12-23 |
| CN105190202B true CN105190202B (en) | 2017-11-17 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201380076370.7A Active CN105190202B (en) | 2013-05-08 | 2013-05-08 | Heat exchanger and refrigerating circulatory device |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US9791189B2 (en) |
| EP (1) | EP2995886A4 (en) |
| JP (1) | JP6109303B2 (en) |
| CN (1) | CN105190202B (en) |
| WO (1) | WO2014181400A1 (en) |
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| WO2015059832A1 (en) * | 2013-10-25 | 2015-04-30 | 三菱電機株式会社 | Heat exchanger and refrigeration cycle device using said heat exchanger |
| JP6415597B2 (en) * | 2014-12-10 | 2018-10-31 | 三菱電機株式会社 | Refrigeration cycle equipment |
| EP3330637B1 (en) * | 2015-07-29 | 2021-08-25 | Mitsubishi Electric Corporation | Heat exchanger and refrigeration cycle apparatus |
| CN107202504B (en) * | 2016-03-17 | 2021-03-30 | 浙江盾安热工科技有限公司 | Cross current conversion device and micro-channel heat exchanger |
| CN209054801U (en) * | 2016-03-31 | 2019-07-02 | 三菱电机株式会社 | Heat exchanger and refrigerating circulatory device |
| JP6380449B2 (en) * | 2016-04-07 | 2018-08-29 | ダイキン工業株式会社 | Indoor heat exchanger |
| WO2018047330A1 (en) * | 2016-09-12 | 2018-03-15 | 三菱電機株式会社 | Air conditioner |
| CN110168294A (en) * | 2017-07-05 | 2019-08-23 | 日立江森自控空调有限公司 | The outdoor heat exchanger of air conditioner and the air conditioner for having the outdoor heat exchanger |
| KR20190032106A (en) * | 2017-09-19 | 2019-03-27 | 엘지전자 주식회사 | Heat exchanger |
| CN110762902A (en) * | 2018-07-26 | 2020-02-07 | 维谛技术有限公司 | Micro-channel evaporator and air conditioning system |
| CN109520355A (en) * | 2018-12-21 | 2019-03-26 | 广东美的白色家电技术创新中心有限公司 | Heat-exchanger rig and refrigeration equipment |
| CN113566311A (en) * | 2021-07-27 | 2021-10-29 | 珠海格力电器股份有限公司 | Heat exchanger and air conditioner |
| JPWO2023032155A1 (en) * | 2021-09-03 | 2023-03-09 |
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| US20160054038A1 (en) | 2016-02-25 |
| WO2014181400A1 (en) | 2014-11-13 |
| US9791189B2 (en) | 2017-10-17 |
| JPWO2014181400A1 (en) | 2017-02-23 |
| EP2995886A1 (en) | 2016-03-16 |
| EP2995886A4 (en) | 2017-02-01 |
| CN105190202A (en) | 2015-12-23 |
| JP6109303B2 (en) | 2017-04-05 |
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